CA2069593A1 - Combined gas/steam power station plant - Google Patents
Combined gas/steam power station plantInfo
- Publication number
- CA2069593A1 CA2069593A1 CA002069593A CA2069593A CA2069593A1 CA 2069593 A1 CA2069593 A1 CA 2069593A1 CA 002069593 A CA002069593 A CA 002069593A CA 2069593 A CA2069593 A CA 2069593A CA 2069593 A1 CA2069593 A1 CA 2069593A1
- Authority
- CA
- Canada
- Prior art keywords
- steam
- gas
- turbine
- power station
- gas turbine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
- F02C6/003—Gas-turbine plants with heaters between turbine stages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2260/00—Function
- F05D2260/20—Heat transfer, e.g. cooling
- F05D2260/211—Heat transfer, e.g. cooling by intercooling, e.g. during a compression cycle
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
Abstract
ABSTRACT OF THE DISCLOSURE
In a combined gas/steam power station plant which consists essentially of a fossil-fired gas turbine group and a steam circuit, with an exhaust heat boiler (11) in between, intercooling and reheat is provided to maximize the efficiency. The gas turbine group consists of two compressors (1, 2), of two combustion chambers (7, 9) and of two turbines (8, 10).
Downstream of the first compressor (1), there is an intercooler (3) and on the cool side of this is placed an evaporator (4) which is in effective connection with the intercooler. The steam quantity formed in the evaporator (4) is introduced into a turbine (6) of the steam circuit, the result of this being a first improvement in efficiency. Downstream of the first turbine (8), there is a second combustion chamber (9) in which the exhaust gases from the first turbine (8) are processed to produce hot gases for the second turbine (10). The large calorific potential still present in the exhaust gases from this second -turbine (10) flows through the exhaust heat boiler (11) in which a maximized steam power is produced, the result of which is the second improvement in efficiency.
In a combined gas/steam power station plant which consists essentially of a fossil-fired gas turbine group and a steam circuit, with an exhaust heat boiler (11) in between, intercooling and reheat is provided to maximize the efficiency. The gas turbine group consists of two compressors (1, 2), of two combustion chambers (7, 9) and of two turbines (8, 10).
Downstream of the first compressor (1), there is an intercooler (3) and on the cool side of this is placed an evaporator (4) which is in effective connection with the intercooler. The steam quantity formed in the evaporator (4) is introduced into a turbine (6) of the steam circuit, the result of this being a first improvement in efficiency. Downstream of the first turbine (8), there is a second combustion chamber (9) in which the exhaust gases from the first turbine (8) are processed to produce hot gases for the second turbine (10). The large calorific potential still present in the exhaust gases from this second -turbine (10) flows through the exhaust heat boiler (11) in which a maximized steam power is produced, the result of which is the second improvement in efficiency.
Description
- 2 ~
28.5.91/ Bo TITLE OF THE INVENTION
Combined gas/steam power station plant BACXGROUND OF THE INVENTION
Field of the Invention -The present invention concerns a combined gas/steam power station plant.
Discussion of Backqround The concept "combined gas/steam power station plant" - referred to below as combined power station for short - is always understood to mean the interactioP of at least one gas turbine group with at least one steam turbine circuit, the exhaust gases from the operation of the gas turbine group belng passed through an exhaust heat steam generator (= exhaust heat boiler) in which the residual heat potential of these exhaust gases is used to generate the steam necessary for admission to the steam turbine. This additional steam power leads to a higher plant thermal efficiency.
These combined power stations therefore have a very good conversion efficiency which is of the order o value of some 50-55%. One possibility of significantly increasing the efficiency of this plant can be an increase in the hot gas temperature. This introduces other disadvantages which have a negative effect on the efficiency of the plant and the economy of the electricity produced, i.e. the specific costs of the plant. It should therefore be noted that the preparation of a hot gas with a temperature of more than 1400 C inevitably involves an advance into a range in which the NOX emissions from this combustion increase abruptly, which, in turn, makes measures such as water or steam injection necessary. These measures :
.. . .
. , 2 ~ 3 substantially negate the efficiency improvement theoretically to ~e expected from the increase in temperature so that the associated gain in efficiency bears no relation to the expenditure required, quite apart from the fact that any increase in temperature involves expensive adaptations with respect to high quality materials and expensive arrangements for cooling, especially as regards the blading.
SUMMARY OF THE INVENTION
Accordingly, one object of this invention is to increase the plant efficiency in a combined ~as/steam power station plant of the type mentioned at the beginning without increasing the temperature of the hot gases.
The essential advantage of the invention may be seen in the fact that with reduced specific plant costs, the efficiency of the combined power station according to the invention can be increased to approximately 60% for a mixture temperature of 1200 C
before the gas turbine. This is achieved, on the one hand, by supplementing the compressor with an intercooler which introduces an increase in the specific power. A consequence of this would be a significant reduction in the combined power station efficiency. This negative effect, however, is obviated by the circuit according to the invention because the heat from the intercooler is usefully employed in such a way that pressurized water is generated which is partially converted into steam in the evaporator. This steam is then introduced into the steam turbine at an appropriate position and participates to the extent of 2-4 points, depending on the pressure ratio, in the combined efficiency. On the other hand, an additional measure is undertaken which provides a further increase in efficiency; this involves heating the compressed air initially, as is usual, in a combustion chamber from approximately 300 C to approximately 1350 C before it 2~6~
is expanded in a high pressure turbine. In this process, the temperature is reduced from a mixed value of 1200 C to approximately 1000 ~C. It is then reheated again to approximately 1400 C in such a way that in the subsequent low pressure turbine, an average turbine inlet temperature of 1200 C again appears.
This has the effect that the combustion gases flowing to the exhaust heat boiler have a temperature of approximately 600 C. The efficiency of the combined plant can be maximized to the circumscribed extent by the interdependence of these two measures.
Advantageous and expedient further developments of the solution according to the invention are given in the dependent claims.
BRIEF DESCRIPTION OF T~E DRAWINGS
A more complete appreciation of the invention and many of the attendant advantages thereof will be readily obtained as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings, wherein:
Fig. 1 shows a circuit diagram of a combined power station with reheat and intercooling and Fig. 2 shows a two-shaft coaxial arrangement of a gas turbine with reheat and intercooling.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings, wherein like reference numerals designate identical or corresponding parts throughout the several views, where the flow direction of the media is indicated by arrows and where all elements not directly necessary for understanding the invention are omitted, Fig. 1 shows a circuit diagram of a combined power station with intercooling and reheat. The compressor stage in this combined power station is subdi~ided into two partial 2~6~3~
compressors 1 and 2. Between these two compressors 1, 2, i.e. downstream of the first compressor 1 and upstream of the second compressor 2, there is an intercooler 3 in which the partially compressed air is intercooled. The hot water generated in this intercooler 3 from the intercooling process mentioned is supplied to a downstream evaporator 4, which can be single-stage or multi-stage. Evaporation occurs here and the steam 20 gained in this manner is supplied to a suitable position in the steam turbine 6, downstream of the gas turbine group. This steam initially participates in the combined efficiency to the extent o~ between 2 and 4 points, depending on the pressure ratio. The compressed air from the compressor 2 passes at, for example, 45 bar into a first hot gas generating plant 7, which is preferably a combustion chamber, in which the air is heated from approximately 350 C to approximately 1350 C hot gas temperature. ~his hot gas is then admitted to a high pressure turbine 8 in which the gas is expanded from 45 bar to approximately 14 bar. The temperature of the hot gas experiences a reduction from a mixed ~alue of 1200 C to approximately 850 C in this high pressure turbine 8.
The exhaust gases from this high pressure turbine 8 are then heated to approximately 1400 C in a second hot gas generating plant 9, which is preferably a combustion chamber, in order to achieve by this means a weighted averaqe turbine inlet temperature of 1200 C
also for a low pressure turbine 10 connected downstream of said second combustion chamber 9. Both the first combustion chamber 7 and the second combustion chamber 9 can be operated with a liquid and/or gaseous fuel.
The cooling air ~lows for the two turbines 8 and 10 are each about 10-15% and are extracted at appropriate locations from the compressors 1, 2. This cannot be seen in Fig. 1. Expansion occurs in the low pressure turbine 10 with a pressure ratio of approximately 14 so that the exhaust gases flowing to an exhaust heat 20~5~
boiler 11 fitted downstream of the turbine last mentioned are at approximately 600 C. Steam is there generated in two pressure stages and is then supplied to the downstream steam turbine 6. It is also possible to use a three-pressure exhaust heat boiler.
Downstream of this steam turbine 6, there is a condenser 12 in which water or air can be used as the cooling medium 13. The condensate of the exhaust steam from the steam turbine 6 is then divided into two partial flows. One partial flow 14 is fed by a supply pump 15 into the exhaust heat boiler 11; the other partial flow 16 flows via a further supply pump 17 through the intercooler 3 and the evaporator 4. In the intercooler 3, the air flowing from the compressor 1 is cooled down to 70 C and the water is heated to approximately 180-200 C in the process. The water is in turn cooled down in the evaporator 4 by the removal of the evaporation heat. The evaporator 4 can also be used as a de-aerator. The gas turbine group and the steam turbine drive one generator each 18, lg. The circuit last described with the second combustion chamber 9, downstream of the high pressure turbine 8 and upstream of the low pressure turbine 10, participates for its part in the combined efficiency to the extent of at least 5 points so that, on the basis of an efficiency yield of approximately 55% -for a combined power station associated with the state of the art, and taking account of the improvement in efficiency ~rom the introduction of the steam 20 gained in the evaporator 4 in the steam turbine 6, an efficiency of at least 60% will be obtained in the circuit described here.
With respect to the arrangement of such a circuit in accordance with Fig. 1, it is suggested that because o~ the large pressure ratio of about 45 or more~ a two-shaft gas turbine should be emplo~ed because the variation in volume flow during the process is very large. In order, furthermore, to keep the compressor 2 0 ~ 3 outlet temperature within bounds, the intercooling of the compression already described with respect to Fig. 1 is provided. The ideal arrangement with respect to fluid logistics is, of course, that with a so-called "core engine", as is proposed in Fig. 2. This involves the central introduction of a power-balanced gas turbine group with compressor, combustion chamber 7 and turbine 8.
Fig. 2 fundamentally shows the same circuit for the gas turbine group as Fig. 1 in the same ideal arrangement with respect to fluid logistics. The main purpose of this two shaft coaxial arrangement is to eliminate hot gas ducts downstream of the first combustion chamber 7 and downstream of the second combustion chamber 9. One possible solution is to design the combustion chambers as annular combustion chambers. What has been said applies, of course, to both combustion chambers, which can be constant volume combustion chambers instead of constant pressure combustion chambers, it being possible to use the individual cells of a cell wheel as the combustion space in the case of constant volume combustion chambers.
The introduction, as mentioned, of an intrinsically power-balanced gas turbine group with compressor 2, combustion cham~er 7 and turbine 8 ~orms a unit whose speed is independent of the speed of the low pressure group (with compressor 1, combustion chamber 9 and turbine 10) and is, generally speaking, higher. The first group can certainly be referred to as a pressure increasing unit. The low pressure unit therefore forms the basic unit. Such a configuration is ideal for a modular system. The basic unit can also be designed for 50 Hz or 60 Hz with approximately the same mass ~low so that the modular system can be extended t~ the maximum extent~
The provision of a single-shaft arrangement is not, of cour~e, excluded for technical reasons. It 2 ~ ~ ~ P ~5 ~
should, however, be noted that in such an arrangement, 2-3 points of efficiency are sacrificed relative to an arranyement optimized in pressure ratio. A reduction in specific power of approximately 15% has to be accepted. On the other hand, there are operational advantages such as a simple control and safety system.
The part-load behavior is not seriously penalized by the single-shaft design with respect to efficiency because very good part-load efficiency behavior is obtained by induction air preheating, possibly combined with adjustment of the compressor inlet guide vane row.
It should also be noted that as a pure gas turbine, i.e. without a downstream steam turbine, reheating gives no advantage in terms of efficiency. On the contrary, a reduction has to be accepted. Intercooling with or without reheat does, however, improve the efficiency to the extent quoted above in the case of large pressure ratios. However, even with reheat alone the specific power increases by some 20%, while wilth reheat and intercooling it increases by as much as approximately two-thirds.
Obviously, numerous modifications and varlations of the present invention are possible in light of the above teachings. It is therefore to be understood that within the scope of the appended claims, the invention may be practised otherwise than as specifically described herein.
28.5.91/ Bo TITLE OF THE INVENTION
Combined gas/steam power station plant BACXGROUND OF THE INVENTION
Field of the Invention -The present invention concerns a combined gas/steam power station plant.
Discussion of Backqround The concept "combined gas/steam power station plant" - referred to below as combined power station for short - is always understood to mean the interactioP of at least one gas turbine group with at least one steam turbine circuit, the exhaust gases from the operation of the gas turbine group belng passed through an exhaust heat steam generator (= exhaust heat boiler) in which the residual heat potential of these exhaust gases is used to generate the steam necessary for admission to the steam turbine. This additional steam power leads to a higher plant thermal efficiency.
These combined power stations therefore have a very good conversion efficiency which is of the order o value of some 50-55%. One possibility of significantly increasing the efficiency of this plant can be an increase in the hot gas temperature. This introduces other disadvantages which have a negative effect on the efficiency of the plant and the economy of the electricity produced, i.e. the specific costs of the plant. It should therefore be noted that the preparation of a hot gas with a temperature of more than 1400 C inevitably involves an advance into a range in which the NOX emissions from this combustion increase abruptly, which, in turn, makes measures such as water or steam injection necessary. These measures :
.. . .
. , 2 ~ 3 substantially negate the efficiency improvement theoretically to ~e expected from the increase in temperature so that the associated gain in efficiency bears no relation to the expenditure required, quite apart from the fact that any increase in temperature involves expensive adaptations with respect to high quality materials and expensive arrangements for cooling, especially as regards the blading.
SUMMARY OF THE INVENTION
Accordingly, one object of this invention is to increase the plant efficiency in a combined ~as/steam power station plant of the type mentioned at the beginning without increasing the temperature of the hot gases.
The essential advantage of the invention may be seen in the fact that with reduced specific plant costs, the efficiency of the combined power station according to the invention can be increased to approximately 60% for a mixture temperature of 1200 C
before the gas turbine. This is achieved, on the one hand, by supplementing the compressor with an intercooler which introduces an increase in the specific power. A consequence of this would be a significant reduction in the combined power station efficiency. This negative effect, however, is obviated by the circuit according to the invention because the heat from the intercooler is usefully employed in such a way that pressurized water is generated which is partially converted into steam in the evaporator. This steam is then introduced into the steam turbine at an appropriate position and participates to the extent of 2-4 points, depending on the pressure ratio, in the combined efficiency. On the other hand, an additional measure is undertaken which provides a further increase in efficiency; this involves heating the compressed air initially, as is usual, in a combustion chamber from approximately 300 C to approximately 1350 C before it 2~6~
is expanded in a high pressure turbine. In this process, the temperature is reduced from a mixed value of 1200 C to approximately 1000 ~C. It is then reheated again to approximately 1400 C in such a way that in the subsequent low pressure turbine, an average turbine inlet temperature of 1200 C again appears.
This has the effect that the combustion gases flowing to the exhaust heat boiler have a temperature of approximately 600 C. The efficiency of the combined plant can be maximized to the circumscribed extent by the interdependence of these two measures.
Advantageous and expedient further developments of the solution according to the invention are given in the dependent claims.
BRIEF DESCRIPTION OF T~E DRAWINGS
A more complete appreciation of the invention and many of the attendant advantages thereof will be readily obtained as the same becomes better understood by reference to the following detailed description when considered in connection with the accompanying drawings, wherein:
Fig. 1 shows a circuit diagram of a combined power station with reheat and intercooling and Fig. 2 shows a two-shaft coaxial arrangement of a gas turbine with reheat and intercooling.
DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring now to the drawings, wherein like reference numerals designate identical or corresponding parts throughout the several views, where the flow direction of the media is indicated by arrows and where all elements not directly necessary for understanding the invention are omitted, Fig. 1 shows a circuit diagram of a combined power station with intercooling and reheat. The compressor stage in this combined power station is subdi~ided into two partial 2~6~3~
compressors 1 and 2. Between these two compressors 1, 2, i.e. downstream of the first compressor 1 and upstream of the second compressor 2, there is an intercooler 3 in which the partially compressed air is intercooled. The hot water generated in this intercooler 3 from the intercooling process mentioned is supplied to a downstream evaporator 4, which can be single-stage or multi-stage. Evaporation occurs here and the steam 20 gained in this manner is supplied to a suitable position in the steam turbine 6, downstream of the gas turbine group. This steam initially participates in the combined efficiency to the extent o~ between 2 and 4 points, depending on the pressure ratio. The compressed air from the compressor 2 passes at, for example, 45 bar into a first hot gas generating plant 7, which is preferably a combustion chamber, in which the air is heated from approximately 350 C to approximately 1350 C hot gas temperature. ~his hot gas is then admitted to a high pressure turbine 8 in which the gas is expanded from 45 bar to approximately 14 bar. The temperature of the hot gas experiences a reduction from a mixed ~alue of 1200 C to approximately 850 C in this high pressure turbine 8.
The exhaust gases from this high pressure turbine 8 are then heated to approximately 1400 C in a second hot gas generating plant 9, which is preferably a combustion chamber, in order to achieve by this means a weighted averaqe turbine inlet temperature of 1200 C
also for a low pressure turbine 10 connected downstream of said second combustion chamber 9. Both the first combustion chamber 7 and the second combustion chamber 9 can be operated with a liquid and/or gaseous fuel.
The cooling air ~lows for the two turbines 8 and 10 are each about 10-15% and are extracted at appropriate locations from the compressors 1, 2. This cannot be seen in Fig. 1. Expansion occurs in the low pressure turbine 10 with a pressure ratio of approximately 14 so that the exhaust gases flowing to an exhaust heat 20~5~
boiler 11 fitted downstream of the turbine last mentioned are at approximately 600 C. Steam is there generated in two pressure stages and is then supplied to the downstream steam turbine 6. It is also possible to use a three-pressure exhaust heat boiler.
Downstream of this steam turbine 6, there is a condenser 12 in which water or air can be used as the cooling medium 13. The condensate of the exhaust steam from the steam turbine 6 is then divided into two partial flows. One partial flow 14 is fed by a supply pump 15 into the exhaust heat boiler 11; the other partial flow 16 flows via a further supply pump 17 through the intercooler 3 and the evaporator 4. In the intercooler 3, the air flowing from the compressor 1 is cooled down to 70 C and the water is heated to approximately 180-200 C in the process. The water is in turn cooled down in the evaporator 4 by the removal of the evaporation heat. The evaporator 4 can also be used as a de-aerator. The gas turbine group and the steam turbine drive one generator each 18, lg. The circuit last described with the second combustion chamber 9, downstream of the high pressure turbine 8 and upstream of the low pressure turbine 10, participates for its part in the combined efficiency to the extent of at least 5 points so that, on the basis of an efficiency yield of approximately 55% -for a combined power station associated with the state of the art, and taking account of the improvement in efficiency ~rom the introduction of the steam 20 gained in the evaporator 4 in the steam turbine 6, an efficiency of at least 60% will be obtained in the circuit described here.
With respect to the arrangement of such a circuit in accordance with Fig. 1, it is suggested that because o~ the large pressure ratio of about 45 or more~ a two-shaft gas turbine should be emplo~ed because the variation in volume flow during the process is very large. In order, furthermore, to keep the compressor 2 0 ~ 3 outlet temperature within bounds, the intercooling of the compression already described with respect to Fig. 1 is provided. The ideal arrangement with respect to fluid logistics is, of course, that with a so-called "core engine", as is proposed in Fig. 2. This involves the central introduction of a power-balanced gas turbine group with compressor, combustion chamber 7 and turbine 8.
Fig. 2 fundamentally shows the same circuit for the gas turbine group as Fig. 1 in the same ideal arrangement with respect to fluid logistics. The main purpose of this two shaft coaxial arrangement is to eliminate hot gas ducts downstream of the first combustion chamber 7 and downstream of the second combustion chamber 9. One possible solution is to design the combustion chambers as annular combustion chambers. What has been said applies, of course, to both combustion chambers, which can be constant volume combustion chambers instead of constant pressure combustion chambers, it being possible to use the individual cells of a cell wheel as the combustion space in the case of constant volume combustion chambers.
The introduction, as mentioned, of an intrinsically power-balanced gas turbine group with compressor 2, combustion cham~er 7 and turbine 8 ~orms a unit whose speed is independent of the speed of the low pressure group (with compressor 1, combustion chamber 9 and turbine 10) and is, generally speaking, higher. The first group can certainly be referred to as a pressure increasing unit. The low pressure unit therefore forms the basic unit. Such a configuration is ideal for a modular system. The basic unit can also be designed for 50 Hz or 60 Hz with approximately the same mass ~low so that the modular system can be extended t~ the maximum extent~
The provision of a single-shaft arrangement is not, of cour~e, excluded for technical reasons. It 2 ~ ~ ~ P ~5 ~
should, however, be noted that in such an arrangement, 2-3 points of efficiency are sacrificed relative to an arranyement optimized in pressure ratio. A reduction in specific power of approximately 15% has to be accepted. On the other hand, there are operational advantages such as a simple control and safety system.
The part-load behavior is not seriously penalized by the single-shaft design with respect to efficiency because very good part-load efficiency behavior is obtained by induction air preheating, possibly combined with adjustment of the compressor inlet guide vane row.
It should also be noted that as a pure gas turbine, i.e. without a downstream steam turbine, reheating gives no advantage in terms of efficiency. On the contrary, a reduction has to be accepted. Intercooling with or without reheat does, however, improve the efficiency to the extent quoted above in the case of large pressure ratios. However, even with reheat alone the specific power increases by some 20%, while wilth reheat and intercooling it increases by as much as approximately two-thirds.
Obviously, numerous modifications and varlations of the present invention are possible in light of the above teachings. It is therefore to be understood that within the scope of the appended claims, the invention may be practised otherwise than as specifically described herein.
Claims (6)
1. Combined gas/steam power station plant, consisting essentially of at least one fossil-fired gas turbine group, at least one steam circuit and at least one exhaust heat boiler, which is fitted downstream of the gas turbine group and to which exhaust gases from the gas turbine group can be admitted, wherein the gas turbine group consists of at least two compressors and at least two gas turbines, wherein an intercooler is placed downstream of the first compressor and an evaporator is placed on the cool side of this intercooler and is in effective connection with it, wherein a steam quantity can be introduced from the evaporator into a steam turbine of the steam circuit, wherein means for hot gas generation are present downstream of the first gas turbine.
2. Combined gas/steam power station plant as claimed in claim 1, wherein the means for hot gas generation is a combustion chamber.
3. Combined gas/steam power station plant as claimed in claims 1 and 2, wherein the gas turbine group consists of a basic unit with first compressor, combustion chamber and gas turbine and of a pressure increasing unit with compressor, combustion chamber and first gas turbine.
4. Combined gas/steam power station plant as claimed in claim 3, wherein the basic unit is of two-shaft design relative to the pressure increasing unit.
5. Combined gas/steam power station plant as claimed in claim 3, wherein the combustion chambers are constant pressure or constant volume plants.
6. Combined gas/steam power station plant as claimed in claim 3, wherein the basic unit can be operated at 50 Hz or 60 Hz with approximately the same mass flow.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4118062A DE4118062A1 (en) | 1991-06-01 | 1991-06-01 | COMBINED GAS / VAPOR POWER PLANT |
| DEP4118062.3 | 1991-06-01 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2069593A1 true CA2069593A1 (en) | 1992-12-02 |
Family
ID=6433017
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002069593A Abandoned CA2069593A1 (en) | 1991-06-01 | 1992-05-26 | Combined gas/steam power station plant |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US5313782A (en) |
| EP (1) | EP0516995B1 (en) |
| JP (1) | JP3162479B2 (en) |
| AT (1) | ATE149633T1 (en) |
| CA (1) | CA2069593A1 (en) |
| CZ (1) | CZ163492A3 (en) |
| DE (2) | DE4118062A1 (en) |
Families Citing this family (46)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA2093683C (en) * | 1992-05-14 | 2002-10-15 | William Miller Farrell | Intercooled gas turbine engine |
| DE4237665A1 (en) * | 1992-11-07 | 1994-05-11 | Asea Brown Boveri | Method for operating a combination system |
| DE4237664A1 (en) * | 1992-11-07 | 1994-05-11 | Asea Brown Boveri | Process for operating a turbocompressor |
| DK171830B1 (en) * | 1995-01-20 | 1997-06-23 | Topsoe Haldor As | Method for generating electrical energy |
| DE19506757A1 (en) * | 1995-02-27 | 1996-08-29 | Abb Management Ag | Combined steam-turbine, gas-turbine power station |
| DE19508018A1 (en) * | 1995-03-07 | 1996-09-12 | Abb Management Ag | Process for operating a power plant |
| DE19536839A1 (en) * | 1995-10-02 | 1997-04-30 | Abb Management Ag | Process for operating a power plant |
| EP1243757B1 (en) | 1997-07-25 | 2005-12-07 | ALSTOM Technology Ltd | Process for operating a power plant |
| US6079197A (en) | 1998-01-02 | 2000-06-27 | Siemens Westinghouse Power Corporation | High temperature compression and reheat gas turbine cycle and related method |
| WO2000034638A1 (en) | 1998-12-11 | 2000-06-15 | Alliedsignal Inc. | Power generation system, and heat exchanger and operating method for a power generation system |
| US6385959B1 (en) | 1999-08-24 | 2002-05-14 | MONTOYA CéSAR AGUILERA | Gas turbine engine with increased fuel efficiency and method for accomplishing the same |
| DE19943782C5 (en) * | 1999-09-13 | 2015-12-17 | Siemens Aktiengesellschaft | Gas and steam turbine plant |
| US6523346B1 (en) | 2001-11-02 | 2003-02-25 | Alstom (Switzerland) Ltd | Process for controlling the cooling air mass flow of a gas turbine set |
| US6644012B2 (en) | 2001-11-02 | 2003-11-11 | Alston (Switzerland) Ltd | Gas turbine set |
| PL351011A1 (en) | 2001-12-03 | 2003-06-16 | Bogdan Bukowski | Method of and apparatus for recuperating heat produced by a combustion engine, in particular a motor-car one |
| WO2003076781A1 (en) * | 2002-03-14 | 2003-09-18 | Alstom Technology Ltd | Power generating system |
| DE10228986A1 (en) | 2002-06-28 | 2004-02-19 | Alstom (Switzerland) Ltd. | Intercooling method and gas turbine system with intercooling |
| US7254951B2 (en) * | 2003-01-07 | 2007-08-14 | Lockwood Jr Hanford N | High compression gas turbine with superheat enhancement |
| US20060225428A1 (en) * | 2005-04-07 | 2006-10-12 | Joseph Brostmeyer | Dual fuel combined cycle power plant |
| CA2618030C (en) | 2005-08-10 | 2014-07-08 | Eribert Benz | A method for operating a gas turbine and a gas turbine for implementing the method |
| US20070130952A1 (en) * | 2005-12-08 | 2007-06-14 | Siemens Power Generation, Inc. | Exhaust heat augmentation in a combined cycle power plant |
| US7770376B1 (en) | 2006-01-21 | 2010-08-10 | Florida Turbine Technologies, Inc. | Dual heat exchanger power cycle |
| KR100847204B1 (en) * | 2006-03-09 | 2008-07-17 | 피티엘중공업 주식회사 | Hybrid jet turbine generation system having the synergy of increasing thermal efficiency |
| ATE540213T1 (en) * | 2006-10-16 | 2012-01-15 | Alstom Technology Ltd | METHOD FOR OPERATING A GAS TURBINE SYSTEM |
| WO2009109446A1 (en) * | 2008-03-05 | 2009-09-11 | Alstom Technology Ltd | Method for regulating a gas turbine in a power plant and power plant to carry out the method |
| US20090301078A1 (en) * | 2008-06-10 | 2009-12-10 | General Electric Company | System for recovering the waste heat generated by an auxiliary system of a turbomachine |
| GB2469043B (en) * | 2009-03-30 | 2011-02-23 | Lotus Car | A reheated gas turbine system having a fuel cell |
| US8164208B2 (en) * | 2009-04-15 | 2012-04-24 | General Electric Company | Systems involving multi-spool generators and variable speed electrical generators |
| CH701803A1 (en) * | 2009-09-03 | 2011-03-15 | Alstom Technology Ltd | Gas turbine group and method for operating such a gas turbine group. |
| US8141336B1 (en) * | 2010-09-08 | 2012-03-27 | General Electric Company | Combined cycle power augmentation by efficient utilization of atomizing air energy |
| JP5655472B2 (en) * | 2010-09-29 | 2015-01-21 | 三浦工業株式会社 | Steam hot water generation system |
| DE102010042792A1 (en) * | 2010-10-22 | 2012-04-26 | Man Diesel & Turbo Se | System for generating mechanical and / or electrical energy |
| US20120223531A1 (en) * | 2011-03-02 | 2012-09-06 | Google Inc. | Generator Selection in a Power Plant |
| US9429044B2 (en) * | 2012-01-13 | 2016-08-30 | Alstom Technology Ltd | Supercritical heat recovery steam generator reheater and supercritical evaporator arrangement |
| CZ304338B6 (en) * | 2012-08-28 | 2014-03-12 | VĂŤTKOVICE POWER ENGINEERING a.s. | Integrated power source employing waste heat |
| US8726629B2 (en) * | 2012-10-04 | 2014-05-20 | Lightsail Energy, Inc. | Compressed air energy system integrated with gas turbine |
| CZ2012779A3 (en) * | 2012-11-13 | 2014-03-12 | VĂŤTKOVICE POWER ENGINEERING a.s. | Device to regulate utilization of waste heat of cooled engines |
| US9624829B2 (en) | 2013-03-05 | 2017-04-18 | Industrial Turbine Company (Uk) Limited | Cogen heat load matching through reheat and capacity match |
| US10036317B2 (en) | 2013-03-05 | 2018-07-31 | Industrial Turbine Company (Uk) Limited | Capacity control of turbine by the use of a reheat combustor in multi shaft engine |
| WO2014158244A2 (en) | 2013-03-14 | 2014-10-02 | Rolls-Royce North American Technologies, Inc. | Intercooled gas turbine with closed combined power cycle |
| US20160069264A1 (en) * | 2013-07-22 | 2016-03-10 | Joseph D. Brostmeyer | Gas turbine engine with turbine cooling and combustor air preheating |
| CN103711587B (en) * | 2013-12-24 | 2016-03-23 | 国电新能源技术研究院 | A kind of high pressure reheating combined cycle generation system of fuel gas-steam and electricity-generating method |
| GB2536876A (en) | 2015-03-23 | 2016-10-05 | Aurelia Turbines Oy | Two-spool gas turbine arrangement |
| GB2536878A (en) | 2015-03-23 | 2016-10-05 | Aurelia Turbines Oy | Multi-spool gas turbine arrangement |
| ES2916455T3 (en) * | 2018-05-22 | 2022-07-01 | Siemens Energy Global Gmbh & Co Kg | Expanded Gas Turbine Procedure with Expander |
| US11920526B1 (en) | 2022-08-12 | 2024-03-05 | Rtx Corporation | Inter-cooled preheat of steam injected turbine engine |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1060268A (en) * | 1954-03-31 | |||
| GB1037360A (en) * | 1963-12-20 | 1966-07-27 | Stal Laval Turbin Ab | Thermal power plant with steam and gas turbines in combination |
| US4896499A (en) * | 1978-10-26 | 1990-01-30 | Rice Ivan G | Compression intercooled gas turbine combined cycle |
| US4550562A (en) * | 1981-06-17 | 1985-11-05 | Rice Ivan G | Method of steam cooling a gas generator |
| DE3343319A1 (en) * | 1982-07-01 | 1985-06-05 | Rudolf Dr. 6800 Mannheim Wieser | Combined gas turbine-steam turbine system or gas turbine system |
| SE453114B (en) * | 1986-04-29 | 1988-01-11 | Asea Stal Ab | SET FOR OPERATION OF A TURBIN DEVICE |
| DE3815993A1 (en) * | 1988-05-10 | 1989-11-23 | Rudolf Dr Wieser | Binary-vapour turbine plant |
| SE468910B (en) * | 1989-04-18 | 1993-04-05 | Gen Electric | POWER SUPPLY UNIT, BY WHICH THE CONTENT OF DAMAGE POLLUTANTS IN THE EXHAUSTS IS REDUCED |
-
1991
- 1991-06-01 DE DE4118062A patent/DE4118062A1/en not_active Withdrawn
-
1992
- 1992-05-08 AT AT92107744T patent/ATE149633T1/en not_active IP Right Cessation
- 1992-05-08 DE DE59208086T patent/DE59208086D1/en not_active Expired - Fee Related
- 1992-05-08 EP EP92107744A patent/EP0516995B1/en not_active Expired - Lifetime
- 1992-05-26 CA CA002069593A patent/CA2069593A1/en not_active Abandoned
- 1992-05-29 CZ CS921634A patent/CZ163492A3/en unknown
- 1992-06-01 JP JP14021892A patent/JP3162479B2/en not_active Expired - Fee Related
-
1993
- 1993-09-10 US US08/127,444 patent/US5313782A/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CZ163492A3 (en) | 1993-01-13 |
| DE4118062A1 (en) | 1992-12-03 |
| DE59208086D1 (en) | 1997-04-10 |
| ATE149633T1 (en) | 1997-03-15 |
| EP0516995A1 (en) | 1992-12-09 |
| JPH05179904A (en) | 1993-07-20 |
| JP3162479B2 (en) | 2001-04-25 |
| EP0516995B1 (en) | 1997-03-05 |
| US5313782A (en) | 1994-05-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5313782A (en) | Combined gas/steam power station plant | |
| US6684643B2 (en) | Process for the operation of a gas turbine plant | |
| US5513488A (en) | Power process utilizing humidified combusted air to gas turbine | |
| US6530224B1 (en) | Gas turbine compressor inlet pressurization system and method for power augmentation | |
| US5884470A (en) | Method of operating a combined-cycle plant | |
| US5133180A (en) | Chemically recuperated gas turbine | |
| EP0932748B1 (en) | Closed loop steam cooled steam turbine | |
| US4829763A (en) | Process for producing power | |
| EP0444913A1 (en) | A gas turbine | |
| EP0150990B1 (en) | Process for producing power | |
| JPH0586898A (en) | Halfopen cycle operation type natural gas steam turbine system | |
| JP2001502399A (en) | Hydrogen fuel power plant | |
| US8833080B2 (en) | Arrangement with a steam turbine and a condenser | |
| WO1995011375B1 (en) | Performance enhanced gas turbine powerplants | |
| JP2009185809A (en) | Method and system for reforming combined-cycle working fluid and promoting its combustion | |
| WO1995011375A3 (en) | Performance enhanced gas turbine powerplants | |
| CA2263036C (en) | Gas turbine combined cycle | |
| JPH03151505A (en) | Gas/steam electric power generating facility | |
| US20020043064A1 (en) | Method for operating a power plant | |
| US6061936A (en) | Synthesis gas expander located immediately upstream of combustion turbine | |
| JP4036914B2 (en) | Power plant operation | |
| US5727377A (en) | Method of operating a gas turbine power plant with steam injection | |
| JP3974208B2 (en) | Power plant operation | |
| US20040011047A1 (en) | Gas turbine and air turbine installation and method of operating a power station installation, in particular a gas turbine and air turbine installation | |
| Digumarthi et al. | Cheng-cycle implementation on a small gas turbine engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Discontinued |